CN101994780B - For the parallel gears unit of wind turbine gear-box - Google Patents

For the parallel gears unit of wind turbine gear-box Download PDF

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Publication number
CN101994780B
CN101994780B CN201010250909.4A CN201010250909A CN101994780B CN 101994780 B CN101994780 B CN 101994780B CN 201010250909 A CN201010250909 A CN 201010250909A CN 101994780 B CN101994780 B CN 101994780B
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CN
China
Prior art keywords
gear
shaft
axle
box
high speed
Prior art date
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Expired - Fee Related
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CN201010250909.4A
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Chinese (zh)
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CN101994780A (en
Inventor
德克-奥拉夫·莱曼
埃尔温·范艾伊恩赫文
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ZF Wind Power Antwerpen NV
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ZF Wind Power Antwerpen NV
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D15/00—Transmission of mechanical power
    • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/70—Bearing or lubricating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/40—Transmission of power
    • F05B2260/403—Transmission of power through the shape of the drive components
    • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • F16H1/08—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes the members having helical, herringbone, or like teeth
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19647—Parallel axes or shafts
    • Y10T74/19651—External type
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19679—Spur

Abstract

The invention provides a kind of parallel gears unit (20) for wind turbine gear-box (30).Parallel gears unit (20) at least comprises lower velocity shaft (21) and high speed shaft (22), each axle (21,22) comprises the gear (23,25) with helical tooth, and the gear (23,25) of each axle (21,22) is suitable for engaging each other.Lower velocity shaft (21) is rotatably supported by roller bearing (24a) and high speed shaft (22) is rotatably supported by sliding bearing (24b).The present invention also provides a kind of and comprises the wind turbine comprising this gear-box (30) according to the gear-box (30) of the parallel gears unit (20) of the embodiment of the present invention and one.

Description

For the parallel gears unit of wind turbine gear-box
Technical field
The present invention relates to a kind of for wind turbine gear-box and the parallel gears unit of more specifically many MW wind turbine gear-boxes.The present invention also provides a kind of and comprises the gear-box of this parallel gears unit and a kind of many MW wind turbine comprising the gear-box with this parallel gears unit.
Background technique
Along with wind energy business becomes more and more important, gearbox principle is studied up hill and dale now.The known principle of wind turbine gear-box can comprise at least one planetary gear unit and the parallel gears unit for the generator that planetary gear unit is connected to wind turbine.
Fig. 1 and Fig. 2 is schematically according to the wind turbine gear-box 1 of a type of prior art.In this example, gear-box 1 comprises a planetary gear unit 2 and twin-stage parallel gears unit 3.Planetary gear unit 2 comprises the planet carrier 4 supporting multiple planetary pinion 5.Planetary gear unit 2 also comprises ring gear 6 and sun gear 7.In the example that Fig. 1 and Fig. 2 provides, twin-stage parallel gears unit 3 comprises lower velocity shaft 8, jack shaft 9 and high speed shaft 10, and these axles are all parallel to each other and each is all rotatably supported by bearing 11.Parallel gears unit 3 also comprises two gears 12,13.Gear 12,13 engages with the small gear 14 on jack shaft 9 and the small gear 15 on high speed shaft 10 respectively.
According to other known principle, wind turbine gear-box 1 can comprise two planetary gear units 2 and a single-stage parallel gears unit 3.This illustrates in figure 3.In the example that Fig. 3 provides, gear-box 1 comprises first planet gear unit 2a, the second planetary gear unit 2b and single-stage parallel gears unit 3.Each in planetary gear unit 2a, 2b includes the planet carrier 4, ring gear 6 and the sun gear 7 that support multiple planetary pinion 5.The parallel gears unit 3 of this example is with the difference of example shown in Fig. 1 and Fig. 2, and it only comprises lower velocity shaft 8 and high speed shaft 10, and does not have jack shaft 9.Lower velocity shaft 8 and high speed shaft 10 are rotatably supported by bearing 11.In this example, parallel gears unit 3 comprises a gear 16, and this gear 16 carries on lower velocity shaft 8 and high speed shaft 10 and this gear 16 engages with the small gear 17 on high speed shaft 10.
At the run duration of wind turbine, in gear-box 1, produce the load acted on axle and planetary pinion and the active force being derived from toe joint synapsis.Bear this load in gear-box and active force current position realizes by using rolling bearing.This bearing is located at the high speed shaft place of the parallel gears unit 3 of such as gear-box 1 and must be born the load being derived from gearing.
Because design turbine gear box time and especially design many MW wind turbine gear-box time, noise behavior is important parameter, so the gear in parallel gears unit 3 is typically provided with the helical tooth with large helix angle.But because this large helix angle, create radial and high axial force, this active force bears by the bearing be located on axle.
The bearing arrangement of such as, high speed shaft in parallel gears unit can be designed to the bearing arrangement of locating or the combination being designed to positioning bearing layout and non-locating bearing arrangement.But there is at least one bearing, this at least one bearing bears the combination of axial load or axial load and radial load.
At run duration, wind turbine and especially many MW wind turbine high power is formed to gear-box 1 and form velocity variations in gear-box 1.Therefore, load and the speed of design can be different from the load of gear-box 1 run duration and speed, namely be different from the load of the prediction of gear-box 1 during the design and speed, and even reverse load can occur.
But for many MW wind turbine, the roller bearing 11 that can commercially obtain no longer may can bear the synthesis load from axial force and radial forces.Especially, on roller bearing 11, axial force can be dangerous.This dynamic behavior can cause bearing damage and therefore cause bearing failure.
The load of equivalence dynamic bearing is determined by following formula:
P≈x·F r+y·F a(1)
Wherein F ractual radial bearing load, F abe actual axle to bearing load, x is radial load coefficient for bearing and y is axial load coefficient for bearing.Coefficient x and y depends on the type of bearing used.In the situation of such as taper roller bearing, x can be 0.4 and y between 1.3 and 1.6, can which illustrate axial load more much higher than the contribution of radial load for the contribution of overall load.
Along with the use of the increase of the through-put power of many MW wind turbine and the gearing with large helix angle, need bearing to have high bearing capacity thus can actual loading be born.But its shortcoming is, along with bearing capacity becomes higher, the size of bearing increases and the very important velocity limit of bearing or top speed reduce.
A lot of wind turbine has the generator run with 1500rpm to 2000rpm, and this 2000rpm is their top speed and is therefore the rated velocity of gearbox shaft.When having the cooperative action power from radial load and axial load, synthesis load can higher than radial load.In these cases, suitable roller bearing can not be found bear and requiring the load under speed.
Summary of the invention
The object of embodiments of the invention is to provide a kind of parallel gears unit for the gear-box in many MW wind turbine, a kind ofly comprises the gear-box of this parallel gears unit and a kind of many MW wind turbine comprising the gear-box with this parallel gears unit.
Utilize and achieve above object according to the method and apparatus of the embodiment of the present invention.
Embodiments of the invention aim to provide a kind of parallel gears unit for wind turbine gear-box, its middle (center) bearing can bear the axial load and radial load that are derived from gears meshing, and still allows the high rotation speed such as between 1500rpm and 2000rpm.
In first aspect, the invention provides a kind of parallel gears unit for many MW wind turbine gear-boxes.Many MW wind turbine refer to the wind turbine of the electric power that can produce more than 1 megawatt.This parallel gears unit comprises at least lower velocity shaft and high speed shaft, and each axle includes the gear with helical tooth, and the gear of each axle is suitable for engaging each other.In parallel gears unit according to the present invention, lower velocity shaft is rotatably supported by roller bearing and high speed shaft is rotatably supported by sliding bearing.
In one aspect, the invention provides a kind of parallel gears unit for many MW wind turbine gear-boxes, this parallel gears unit comprises at least two parallel axes, each axle includes the gear with helical tooth, the gear of each axle is suitable for engaging each other, and at least one in axle is supported by roller bearing and at least one other axle is supported by sliding bearing.
It must be understood that, as known to a person skilled in the art, sliding bearing can also be referred to as friction bearing, sliding-type bearing, plain bearing or shaft bearing.
According to embodiments of the invention, this parallel gears unit may further include the jack shaft in the middle of lower velocity shaft and high speed shaft.This jack shaft is rotatably supported by roller bearing.
According to further embodiment, this parallel gears unit may further include the thrust collar at least one in axle, and this thrust collar contacts the gear on adjacent shaft thus.Such as, comprise lower velocity shaft and high speed shaft at parallel gears unit, and thrust collar is located in the situation on high speed shaft, the gear on this thrust collar contact lower velocity shaft.
According to embodiments of the invention, this thrust collar can be at least located on the high speed shaft that supported by sliding bearing.
In an embodiment of the present invention, this thrust collar can contact with the direct geared on adjacent shaft.Thrust collar contacts the gear centre referred on thrust collar and adjacent shaft and there are not other parts with the direct geared on adjacent shaft.
According to other embodiments of the invention, this thrust collar can with the gear mediate contact on adjacent shaft.Gear mediate contact on thrust collar and adjacent shaft refers in the middle of the gear on thrust collar and adjacent shaft can exist other parts, such as wear ring.
This thrust collar can have at 0.8 × d 0with 1.4 × d 0between contact diameter and at 0.1 × d 0with 0.3 × d 0between width, here
d 0＝z·m n(2)
Wherein z is the number of tooth and m nit is normal module.
Thrust collar chamfering between 0 ° and 15 °, such as, between 0.5 ° and 5 ° or between 0.5 ° and 2.5 °, and can be such as 1 °.
Roller bearing can be selected from the list comprising taper roller bearing, cylindrical roller bearing, spherical roller bearing or CARB toroidal roller bearings.When this parallel gears unit comprises lower velocity shaft, jack shaft and high speed shaft, according to embodiments of the invention, each in jack shaft and lower velocity shaft supports by roller bearing.According to embodiments of the invention, different roller bearings can be selected for jack shaft and lower velocity shaft.According to other embodiments of the invention, identical roller bearing can be selected for jack shaft and lower velocity shaft.
In a word, in a first aspect of the present invention, provide a kind of parallel gears unit for wind turbine gear-box, this parallel gears unit at least comprises lower velocity shaft and high speed shaft, each axle in described lower velocity shaft and described high speed shaft comprises the gear with helical tooth, the gear of an axle in described lower velocity shaft and described high speed shaft and the gear of another axle are suitable for engaging each other, wherein, described lower velocity shaft is rotatably supported by the first roller bearing, and described high speed shaft is rotatably supported by sliding bearing, wherein said parallel gears unit is also included in the thrust collar at least one axle in described lower velocity shaft and described high speed shaft, this thrust collar contacts the gear on adjacent shaft thus, the side mediate contact of the gear on wherein said thrust collar and described adjacent shaft.
Of the present invention further in, provide a kind of gear-box for wind turbine.This gear-box comprises the parallel gears unit with at least lower velocity shaft and high speed shaft, each axle includes the gear with helical tooth, the gear of each axle is suitable for engaging each other, and wherein this lower velocity shaft is rotatably supported by roller bearing and this high speed shaft is rotatably supported by sliding bearing.
Namely, provide a kind of gear-box for wind turbine, this gear-box comprises at least one planetary gear unit and parallel gear unit, wherein, described parallel gears unit comprises at least two parallel axes, each axle in described two parallel axes comprises the gear with helical tooth, the gear of an axle in described two parallel axes and the gear of another axle are suitable for engaging each other, the first axle in wherein said two parallel axes is supported by the first roller bearing and the second axle is supported by sliding bearing, wherein said parallel gears unit is also included in the thrust collar at least one axle in described two parallel axes, this thrust collar contacts the gear on adjacent shaft thus, the side mediate contact of the gear on wherein said thrust collar and described adjacent shaft.
This parallel gears unit may further include the jack shaft in the middle of lower velocity shaft and high speed shaft, and this jack shaft is supported by roller bearing.
According to favourable embodiment, the parallel gears unit in gear-box may further include the thrust collar at least one in axle.
According to specific embodiments, this thrust collar can be at least located on the high speed shaft that supported by sliding bearing.
In the present invention further, provide a kind of wind turbine comprising gear-box according to an embodiment of the invention.This wind turbine can be many MW wind turbine.Many MW wind turbine refer to the wind turbine of the electric power that can produce more than 1 megawatt.
This wind turbine comprises the gear-box with at least one planetary gear unit and parallel gear unit, this parallel gears unit comprises at least lower velocity shaft and high speed shaft, each axle includes the gear with helical tooth, the gear of each axle is suitable for engaging each other, and wherein this lower velocity shaft is rotatably supported by roller bearing and this high speed shaft is rotatably supported by sliding bearing.
Combine with accompanying drawing, according to following detailed description, above and other characteristic of the present invention, feature and advantage will become obvious, and this accompanying drawing illustrates principle of the present invention by example.
Accompanying drawing explanation
Fig. 1 to Fig. 3 signal is according to the gearbox principle of prior art.
Fig. 4 and Fig. 5 signal is according to the parallel gears unit of the embodiment of the present invention.
The thrust collar that Fig. 6 signal can use together with parallel gears unit according to an embodiment of the invention.
Fig. 7 to Figure 11 signal is according to the parallel gears unit of the embodiment of the present invention.
Figure 12 to 14 signals according to the gear-box of the embodiment of the present invention.
Same reference numerals in various figures quotes identical or similar element.
Embodiment
With reference to some non-limitative drawings, the present invention will be described about specific embodiment.It must be understood that and the present invention is not limited thereto.In order to schematic object, the size of some elements in the drawings proportionally may not drawn by exaggerating.
Term such as " comprises " and " connection " is not construed as limiting the present invention by any way.The term used " comprises " and should not be construed as being limited to the device after this listed; It does not get rid of other element or step.Similarly, should notice that the term " connection " used should not be construed as being limited to only directly connecting.
That although embodiments more described here comprise some but not other the feature comprised in other embodiments, but the Feature Combination of different embodiment means within the scope of the invention and forms different embodiments, as it will be understood to those of skill in the art that.Such as, any claimed embodiment can be combinationally used with any.
Hereinafter, will different embodiments be utilized to describe the present invention.It must be understood that, these embodiments are only used to easy to understand the present invention and not intended to be limits the present invention by any way.
The invention provides a kind of parallel gears unit for the gear-box in many MW wind turbine, a kind ofly comprise the gear-box of this parallel gears unit and a kind of many MW wind turbine comprising this gear-box.Many MW wind turbine refer to the wind turbine of the electric power that can produce more than 1 megawatt.
Previously described at run duration, wind turbine and especially many MW wind turbine at run duration high power is formed to gear-box and form velocity variations in gear-box.This dynamic behavior can cause bearing damage and therefore cause bearing failure.One of possible reason of bearing failure can due to the axial motion of the roller in dynamically the causing of axial force and these axial forces, bearing.Therefore, on the top acting on the radial load on bearing, these axial forces can bring out the axial vibration of bearing.
And then noise behavior is identified as the important parameter in the design of many MW wind turbine gear-box.In order to the behavior of optimization noise, the parallel gears unit of gear-box is designed to the helical tooth with having large helix angle.This large helix angle causes high radial load and the formation of axial load.In order to bear the actual loading in this many MW wind turbine gear-box, need the bearing with high bearing capacity.But for higher bearing load carrying capacity, the size of bearing increases and the maximum speed limit of bearing or top speed reduce.
For many MW wind turbine, the combination load from axial force and radial forces may can not be born for the available roller bearing in the parallel gears unit of gear-box, therefore, other cod may be needed compensate the axial force of the helical tooth being derived from gear.And then even if this available roller bearing can partially or fully bear axial force and radial forces, they can not realize it under high rotation speed needed for such as between 1500rpm and 2000rpm.
Therefore, present invention teaches the axle using suitable bearing arrangement for rotatably supports parallel gear unit.
In one aspect, the invention provides a kind of parallel gears unit for many MW wind turbine gear-boxes.Many MW wind turbine refer to the wind turbine of the electric power that can produce more than 1 megawatt.This parallel gears unit comprises at least lower velocity shaft and high speed shaft, and each axle includes the gear with helical tooth, and the gear of each axle is suitable for engaging each other.This lower velocity shaft is rotatably supported by roller bearing and this high speed shaft is rotatably supported by sliding bearing.
It must be understood that, as known to a person skilled in the art, sliding bearing can also be referred to as friction bearing, sliding-type bearing, plain bearing or shaft bearing.
In parallel gears unit according to an embodiment of the invention, the bearing arrangement on axle can bear the load produced at the run duration of gear-box, still allows the high rotation speed such as between 1500rpm and 2000rpm simultaneously.
Fig. 4 signal is according to a part for the parallel gears unit 20 of the embodiment of the present invention.In given example, parallel gears unit 20 comprises the first axle 21 and the second axle 22 be parallel to each other.As has been described above, the parallel gears unit 20 of gear-box can comprise lower velocity shaft, jack shaft and high speed shaft or can comprise lower velocity shaft and high speed shaft in the situation of single-stage parallel gears unit in the situation of twin-stage parallel gears unit.Such as, with reference to figure 4, the first axle 21 can be the lower velocity shaft of parallel gears unit 20 and the second axle 22 can be the high speed shaft of parallel gears unit 20.Or the first axle 21 can be the jack shaft of parallel gears unit 20 and the second axle 22 can be the high speed shaft of parallel gears unit 20.
Must be pointed out, as known to a person skilled in the art, lower velocity shaft can also be referred to as low speed jack shaft and jack shaft can also be referred to as high speed jack shaft.
Hereinafter, by utilize be lower velocity shaft the first axle 21 and be that the second axle 22 of high speed shaft further describes the present invention.It must be understood that this is only used to be easy to explain and not intended to be limits the present invention by any way.Are other embodiments of the invention of twin-stage parallel gears unit according to wherein parallel gears unit 20, the first axle 21 can also be jack shaft.
In the example that Fig. 4 provides, lower velocity shaft 21 is coupled to the first gear 23 and is rotatably supported by roller bearing 24a.First gear 23 can also be referred to as gearwheel, and is specifically referred to as low speed gearwheel.Gear 23 has helical tooth and has diameter d 1.High speed shaft 22 is coupled to second gear 25 that can also be referred to as small gear, and is supported by sliding bearing 24b.Second gear or small gear 25 also have helical tooth.Second gear 25 engages with the first gear 23 and has diameter d 2, this diameter d 2be less than the diameter d of the first gear 23 1.
In the drawings, for ease of signal, sliding bearing 24b is drawn into two rectangles.It must be understood that, can also as schematically drawn sliding bearing 24b in further detail in the illustration of Fig. 4.
Roller bearing 24a can be the roller bearing 24a of well known by persons skilled in the art, any kind, such as taper roller bearing, cylindrical roller bearing, spherical roller bearing or CARB toroidal roller bearings (see further instruction).In the diagram, the roller bearing 24a supporting lower velocity shaft 21 is the cylindrical roller bearing being arranged in O position.
Comprise in the situation of lower velocity shaft 21, high speed shaft 22 and jack shaft at parallel gears unit 20, according to embodiments of the invention, both lower velocity shaft 21 and jack shaft are all rotatably supported by roller bearing 24a, and high speed shaft 22 is rotatably supported by sliding bearing.In this case, according to embodiments of the invention, the type supporting the roller bearing 24a of lower velocity shaft 21 can be identical with the type of the roller bearing 24a supporting jack shaft.According to further embodiment, the type supporting the roller bearing 24a of lower velocity shaft 21 can be different from the type of the roller bearing 24a supporting jack shaft.
In the drawings, the outer cover of reference numerals 27 schematically gear-box.
According to embodiments of the invention, parallel gears unit 20 may further include thrust collar 26.Thrust collar 26 can be located at least one in lower velocity shaft 22, jack shaft or high speed shaft 21.Fig. 5 signal is according to the parallel gears unit 20 of this embodiment.In this example, thrust collar 26 is located on high speed shaft 21, and this high speed shaft 21 is supported by sliding bearing 24b and comprises gear 25, and this gear 25 has the diameter d being less than gearwheel 23 1diameter d 2.But according to other embodiments of the invention, thrust collar 26 can also be located on lower velocity shaft 21, this lower velocity shaft 21 is supported by roller bearing 24a and comprises gear 23, and this gear 23 has the diameter d higher than small gear 25 2diameter d 1(see further instruction).
The combination of bearing arrangement suitable as mentioned above and the use of thrust collar at least one axle such as high speed shaft of parallel gears unit 20 provide for being derived from bearing of the axial load of gears meshing and the suitable of radial load, still allow the high rotation speed such as between 1500rpm and 2000rpm simultaneously.
An advantage of the present embodiment is, because the axial force that the helical tooth of gear produces directly is born by thrust collar, so other cod is on each axle unnecessary.Therefore, respectively back shaft 21 with 22 roller bearing 24a do not suffer high axial force with sliding bearing 24b or will at least more lightly suffer this axial force compared with prior art bearing.Therefore, roller bearing 24a and sliding bearing 24b can have the longer life-span.
Another effect of thrust collar is provided to be because axial force is bear in little loop in gear, so reduce in outer cover, usually serious axial load according to embodiments of the invention.This uses lightweight material or the possibility thick compared with thin-walled by providing when the outer cover of design gear case.
Fig. 6 signal can at an example according to the thrust collar 26 used in the parallel gears unit 20 of the embodiment of the present invention.It must be understood that this is only an example and not intended to be limits the present invention by any way.The side view illustrating this thrust collar 26 located on the left of Fig. 6 and in figure 6 between the top view illustrating this thrust collar 26.Thrust collar 26 can have at 0.8 × d 0with 1.4 × d 0between contact diameter d c(see Fig. 5) and at 0.1 × d 0with 0.3 × d 0between width w c, here
d 0＝z·m n，
Wherein z is the number of tooth and m nit is normal module.
The right part of flg signal of Fig. 6 is as the part A illustrated in the left hand view of Fig. 6.Can see that thrust collar 26 comprises thrust collar chamfering X from this right part of flg.Thrust collar chamfering X between 0 ° and 15 °, such as, between 0.5 ° and 5 ° or between 0.5 ° and 2.5 °, and can be such as 1 °.Because there is thrust collar chamfering X, so thrust collar 26 can have the first contact diameter d c1with the second contact diameter d c2, wherein d c1be less than d c2.At d c1and d c2between difference be determined by the size of thrust collar chamfering X.
In the embodiment of Fig. 5 signal, thrust collar 26 is configured to the gear of adjacent shaft, directly contacts at the gearwheel 23 provided in example.Thrust collar 26 and gearwheel 23 directly contact to refer to does not exist other parts any in the middle of thrust collar 26 and gearwheel 23.
But according to other embodiments of the invention, thrust collar 26 can be configured to and gearwheel 23 mediate contact, thrust collar 26 and gearwheel 23 mediate contact refer to exists other parts, such as wear ring in the middle of thrust collar 26 and gearwheel 23.According to embodiments of the invention, wear ring 28 can such as have at 0.8 × d 0with 1.4 × d 0between outer diameter D w, here
d 0＝z·m n，
Wherein z is the number of tooth and m nit is normal module.
Hereinafter, some examples according to the implementation of the parallel gears unit 20 of the embodiment of the present invention will be described.It must be understood that this is only that not intended to be limits the present invention by any way by example and in order to the object illustrated.
In the figure 7, lower velocity shaft 21 is supported by taper roller bearing 24a and high speed shaft 22 is supported by sliding bearing 24b.There is not any thrust housing cam 26.
Fig. 8 signal and implementation similar in the figure 7.Lower velocity shaft 21 is supported by taper roller bearing 24a and high speed shaft 22 is supported by sliding bearing 24b.Difference between example in this example and Fig. 7 is, in this example, high speed shaft 22 arranges thrust collar 26.Thrust collar 26 directly contacts with gearwheel 23.In this example, taper roller bearing 24a is arranged in X position.
In fig .9, lower velocity shaft 21 by cylindrical roller bearing 24a support and high speed shaft 22 supported by sliding bearing 24b.In this example, the cylindrical roller bearing 24a on lower velocity shaft 21 is set with X configuration.Thrust collar 26 is located on high speed shaft 22.Thrust collar 26 directly contacts with gearwheel 23.
In Fig. 10, lower velocity shaft 21 is supported by taper roller bearing 24a and high speed shaft 22 is supported by sliding bearing 24b.Be with the difference of Fig. 8, in this example, taper roller bearing 24a is arranged in O position.Thrust collar 26 is located on high speed shaft 21.Thrust collar 26 directly contacts with small gear 25.
In fig. 11, be similar to Fig. 8, lower velocity shaft 21 is supported by the taper roller bearing 24a in X position, and high speed shaft 22 is supported by sliding bearing 24b.Thrust collar 26 is located on lower velocity shaft 21.Thrust collar 26 directly contacts with small gear 25.
It must be understood that, in the above example, lower velocity shaft 21 can be supported by the roller bearing 24a of any type as above.And then any combination of the roller bearing 24a on lower velocity shaft 21 and the sliding bearing 24b on high speed shaft 22 can be combined by with the thrust collar 26 on the gear 23 be located on lower velocity shaft 21 or by with the thrust collar 26 on the gear 25 be located on high speed shaft 22.In addition, any this combination can be combined by with the wear ring 28 existed in an alternate manner in the middle of gear 23,25 and thrust collar 26.
And then it must be understood that, in the above example, the first axle is referred to as lower velocity shaft 21.As addressed before, according to embodiments of the invention, the first axle 21 can also realize as the jack shaft of parallel gears unit 20.
In second aspect, the invention provides a kind of gear-box 30 for many MW wind turbine.Gear-box 30 comprises at least one planetary gear unit 31 and parallel gear unit 20.Parallel gears unit 20 comprises at least lower velocity shaft 21 and high speed shaft 22, and each axle 21,22 includes the gear 23,25 with helical tooth, and the gear 23,25 of each axle 21,22 is suitable for engaging each other.Lower velocity shaft 21 is rotatably supported by roller bearing 24a and high speed shaft 22 is rotatably supported by sliding bearing 24b.Can realize according to the parallel gears unit 20 in the gear-box 30 of the embodiment of the present invention in all modes described about a first aspect of the present invention above.
The gear-box 30 of Figure 12 signal the first embodiment according to a second aspect of the present invention.Gear-box 30 comprises outer cover 27, planetary gear unit 31 and twin-stage parallel gears unit 20.Planetary gear unit 31 comprises the planet carrier 32 supporting multiple planetary pinion 33.Planetary pinion 33 engages with sun gear 34 and ring gear 35.According to the first embodiment, twin-stage parallel gears unit 20 comprises lower velocity shaft 21, jack shaft 36 and high speed shaft 22.Lower velocity shaft 21 and jack shaft 36 are rotatably supported by roller bearing 24a.High speed shaft 22 is rotatably supported by sliding bearing 24b.
According to embodiments of the invention, thrust collar 26 can be located at least one in the axle 21,22,36 of parallel gears unit 20.Figure 13 illustrates an example of gear-box 30, and wherein in parallel gears unit 20, thrust collar 26 is located on high speed shaft 22.
According to further embodiment of the present invention, wear ring 28 can be there is in gear 23,25 centre of thrust collar 26 and adjacent shaft.
And then the parallel gears unit 20 in the gear-box 30 illustrated in Figure 12 or Figure 13 can be any parallel gears unit 20 as described in the embodiment of a first aspect of the present invention.
The gear-box 30 of Figure 14 signal the second embodiment according to a second aspect of the present invention.Gear-box 30 comprises two planetary gear unit 31a and 31b and single-stage parallel gears unit 20.Each in planetary gear unit 31a with 31b include with in a first embodiment about the identical parts that planetary gear unit 31 describes.Parallel gears unit 20 comprises lower velocity shaft 21 and high speed shaft 22.Lower velocity shaft 21 is rotatably supported by roller bearing 24a and high speed shaft 22 is rotatably supported by sliding bearing 24b.
Thrust collar 26 is located on high speed shaft 22.But according to other embodiment, thrust collar 26 can also be located on lower velocity shaft 21.According to the further embodiment of the present invention, thrust collar 26 can be saved.Or, according to further embodiment, wear ring 28 can be there is in the middle of the gear 23,25 of thrust collar 26 and adjacent shaft.
Again, the parallel gears unit 20 that it must be understood that in the gear-box 30 illustrated in fig. 14 can be any parallel gears unit 20 as described in the embodiment of first aspect present invention.
In the third aspect, the present invention also provides a kind of wind turbine, and this wind turbine comprises the gear-box 30 according to the embodiment of the present invention.Preferably, this wind turbine can be many MW wind turbine.Many MW wind turbine refer to the wind turbine of the electric power that can produce more than 1 megawatt.Gear-box 30 can comprise at least one planetary gear unit 31 and parallel gear unit 20.Parallel gears unit 20 at least comprises lower velocity shaft 21 and high speed shaft 22, and each axle 21,22 includes the gear 23,25 with helical tooth, and the gear 23,25 of each axle 21,22 is suitable for engaging each other.Lower velocity shaft 21 is rotatably supported by roller bearing 24a and high speed shaft 22 is rotatably supported by sliding bearing 24b.
It must be understood that, gear-box 30 in wind turbine can be any gear-box 30 as described about second aspect present invention, this gear-box comprises parallel gears unit 20, and this parallel gears unit 20 can be the arbitrary parallel gears unit 20 as described in the embodiment of first aspect present invention.

Claims (9)

1. one kind for the parallel gears unit (20) of wind turbine with gear-box (30), this parallel gears unit (20) at least comprises lower velocity shaft (21) and high speed shaft (22), each axle in described lower velocity shaft (21) and described high speed shaft (22) comprises the gear (23,25) with helical tooth, the gear of an axle in described lower velocity shaft (21) and described high speed shaft (22) and the gear of another axle are suitable for engaging each other, wherein
Described lower velocity shaft (21) is rotatably supported by the first roller bearing (24a), and described high speed shaft (22) is rotatably supported by sliding bearing (24b),
Wherein said parallel gears unit (20) is also included in the thrust collar (26) at least one axle in described lower velocity shaft (21) and described high speed shaft (22), this thrust collar (26) contacts the gear (25,23) on adjacent shaft thus
The side mediate contact of the gear (25,23) on wherein said thrust collar (26) and described adjacent shaft.
2. parallel gears unit according to claim 1, wherein said parallel gears unit (20) is also included in the jack shaft (36) in the middle of described lower velocity shaft (21) and described high speed shaft (22), and this jack shaft (36) is rotatably supported by the second roller bearing.
3. parallel gears unit (20) according to claim 1, wherein said thrust collar (26) is at least located on the described high speed shaft (22) that supported by described sliding bearing (24b).
4., in the middle of the gear (25,23) wherein on described thrust collar (26) and described adjacent shaft, there is wear ring (28) in parallel gears unit (20) according to claim 1.
5. parallel gears unit (20) according to claim 2, wherein said first roller bearing (24a) and described second roller bearing are selected from taper roller bearing, cylindrical roller bearing, spherical roller bearing or CARB toroidal roller bearings.
6. the gear-box for wind turbine (30), this gear-box comprises at least one planetary gear unit (31) and parallel gear unit (20), wherein, described parallel gears unit (20) comprises at least two parallel axes, each axle in described two parallel axes comprises the gear (23,25) with helical tooth, the gear of an axle in described two parallel axes and the gear of another axle are suitable for engaging each other, wherein
The first axle in described two parallel axes is supported by the first roller bearing (24a) and the second axle is supported by sliding bearing (24b),
Wherein said parallel gears unit (20) is also included in the thrust collar (26) at least one axle in described two parallel axes, and this thrust collar (26) contacts the gear (25,23) on adjacent shaft thus,
The side mediate contact of the gear (25,23) on wherein said thrust collar (26) and described adjacent shaft.
7. gear-box according to claim 6 (30), wherein said parallel gears unit (20) is also included in the jack shaft (36) in the middle of described first axle and described second axle, and this jack shaft (36) is supported by the second roller bearing.
8. gear-box according to claim 6 (30), wherein said thrust collar (26) is at least located on described second axle that supported by described sliding bearing (24b).
9. a wind turbine, comprises the gear-box (30) any one of claim 6 to 8.
CN201010250909.4A 2009-08-10 2010-08-10 For the parallel gears unit of wind turbine gear-box Expired - Fee Related CN101994780B (en)

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EP2284420A1 (en) 2011-02-16
ES2384022T3 (en) 2012-06-28
US8578806B2 (en) 2013-11-12
AU2010206048B2 (en) 2015-06-04
DK2284420T3 (en) 2012-07-30
ATE554314T1 (en) 2012-05-15
AU2010206048A1 (en) 2011-02-24
US20110033299A1 (en) 2011-02-10
CA2711189A1 (en) 2011-02-10
EP2284420B1 (en) 2012-04-18
CN101994780A (en) 2011-03-30

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